Electropneumatic brake



li j-fi. :17, I Q, R 35 2 2687 ELECTROPNEUMATIC BRAKE Filed July 7, 1934 5 Sheets-Sheet 2 Fig. .265 T I 1%3.

ELE'ASE' FULL SERVICE. INVENTOR CLYDE C FARR/ER SERVICE. ZONEY A7701?" EY RELEASE @e@. 17 11935. c. c. FARMER ELECTROPNEUMATIC BRAKE Filed July 7, 1954 3 Sheets-Sheet 3 Wag. G5.

/88 INVENTOR CLYDE C. FAHMEH A TTORNE Y Patented Dec. 17, 1935 UNITED STATES PATENT OFFICE ELECTROPNEUMATIC BRAKE Application July 7, 1934, Serial No. 734,127

7 Claims.

My invention relates to electropneumatic brake equipment for vehicles and more particularly to such equipment for multiple unit railway trains in which means is provided for varying the braking pressure on the individual cars or trucks in accordance with the load thereon.

It is an object of my invention to provide a light weight brake equipment that is low in cost and simple in construction for use on multiple 1 unit trains in which a uniform fast application and release'of the brakes may be obtained on all cars or train units.

It is another object of my invention to provide a brake equipment which effects a uniform rate of retardation on all train units regardless of the cading thereon.

It is a further object of my invention to provide an electropneumatic brake equipment in which a magnet valve device is provided on each car or truck unit for controlling the supply of fluid under pressure to the brake cylinder and in which means is provided for varying the brake cylinder ressure in accordance with the load on the vehicle.

It is a further object of my invention to provide an electropneumatic brake equipment in which a pneumatic emergency brake application is available in the event of failure of the electrical equipment.

other objects and advantages of my invention will be apparent from the following description of one preferred embodiment thereof taken in connec -on with the accompanying drawings in which Fig. 1 is a diagrammatic View illustrating circuits and apparatus comprising one preferred embodiment of my invention,

Fig. 2 is a diagrammatic sectional view of the self-lapping brake valve device shown in Fig. 1,

3 is a plan view of a portion of the brake valve device shown in Fig. 2,

Fig. 4 is a sectional view taken on the line 4-4 of Fig. 2,

Fig. 5 is a sectional view taken on the line 5-5 of Fig. 2,

Fig. 6 is a diagrammatic sectional view illustrating the control valve shown in Fig. 1,

Fig. 7 is a View taken along the line l'! of Fig. l, and

Fig. 8 is a diagrammatic view illustrating a modified electric circuit.

Referring to the drawings, and more particularly to Fig. 1 thereof, in which brake apparatus is illustrated as employed on two train units, the apparatus comprises a brake cylinder I through which the brakes are applied in accordance with the flow of fluid under pressure from the supply reservoir 2 in accordance with the operation of a control valve device 3 that is governed in accordance with the operation of a self-lapping 5 magnet valve device 4 adapted to be energized from a constant voltage source of electrical energy 5 and controlled by a pressure operated rheostat 6 in accordance with the operation of a self-lapping brake valve device 1. 10

' A supply pipe 8 extends from the brake valve device "I throughout the length of the train and is provided with branch pipe connections to the control valve devices 3 for supplying fluid under pressure to the respective supply reservoirs 2 on the individual train units. The supply pipe 8 is supplied with fluid under pressure from the main reservoir 9, carried on the first unit of the train at the reduced pressure as supplied by feed valve device H. An emergency pipe l2 extends from 5 the brake valve device 1 throughout the length of the train and is provided with branch pipes to the control valve devices 3 carried on each train unit. A train wire l3 extends from the pressure cperated rheostat i5 throughout the length of the train for controlling the energization of the several self-lapping magnet valve devices l, one of which is associated with each train unit. A variable load brake mechanism M is provided on each train unit, for adjusting the degree of energization of the self lapping magnet valve 4 associated with that train unit, upon a particular operation of the pressure rheosLat #3, in accordance with the loadon that unit.

The brake valve device 1, best shown in Figs. 2, 3, l, and 5, may correspond to United States application of Ewing K. Lynn and Rankin J. Bush, for Improvements in brake valve devices, Serial No. 569,158, filed October 16, 1931, and assigned to the same assignee as this application.

The brake valve device 7, best shown in Figs.

2, 3, 4, and 5, comprises a main body portion It, a valve portion [5, a bracket portion 18, and a top or cover portion H. The main body portion, the valve portion, and the bracket portion together define a pressure chamber 18 that is in open communication through the passage and pipe I9 with a pressure controlled rheostat 6. The valve portion I5 is provided with a supply valve chamber 28 that is in open communication through the passage 21 with the supply pipe 8. A supply valve 22 is contained within the supply valve chamber 20 and is slidably disposed within the bushing sleeve 23 to engage a seat 24 carried by the valve portion casing. The valve 22 is subject to the pressure of a spring 25, one end of which engages the valve, and the other end of which engages a nut 26 screw-threadedly attached within a bore in the valve portion casing.

The valve section l5 of the casing is also provided with a cylinder 3| which is open at one end to the pressure chamber |8, the other end of the cylinder being closed by an adjusting member 32 screw-threadedly attached within a bore in the casing section. The adjusting member 32 is provided with a central bore 33 which at its outer end is tapped to receive a screw-threaded cap member 34.

Operatively mounted in the cylinder 3|, adjacent to its open end, is a movable abutment in the form of a piston 35 having a stem 36 which is slidably guided by the adjustable member 32 within the inner end of the bore 33. At one end of the piston 35 is a chamber 31 which is constantly open to the atmosphere through a passage 38. A coil spring 39 is contained in the chamber 31 and is interposed between and engages the inner face of the piston 35 and the inner face of the adjusting member 32.

A release valve chamber 40 is provided within the piston 35, and is in open communication with the pressure chamber 8 through a passage 4|. A release valve 42 is contained within the valve chamber 40, and is adapted to seat on a valve seat 43 formed on the piston, and which is operative to control communication between the valve chamber 46 and the chamber 31, through connecting passage 44 in the piston stem 36. The release valve is provided with a stem 45 the smaller end of which slides within the bore in the stem of the piston 35, and the larger end of which is provided with a collar 46 which slidably engages the piston within a central bore 41 and is subject to the pressure of a release valve spring 48 interposed between and engaging the collar 46 and an annular flange 49 on the piston. Outward movement of the release valve relative to the piston 35 is limited by the collar 46 which engages a stop plate 50 that is secured to the piston 35. The outer end portion of the valve stem 45 extends through an opening in the stop plate 50 and beyond the face of the piston, and is adapted to be operatively engaged by a mechanism that will now be described.

A mechanism is'provided for controlling the operation of the supply valve 22 and the release valve 42 comprising spaced levers 5| that are pivotally mounted intermediate their ends to a pin 52, supported in a plunger 53 that is slidably guided within a bore 54 in the casing section |5.

The lower ends of the spaced levers 5| are connected together by a pin 55, upon which is loosely mounted a roller 56 that is adapted to operatively engage the outer end of the release valve stem 45. The upper ends of the spaced levers 5| are connected together by a pin 51, on which one end of an operating rod 58 is pivotally mounted, the opposite end of the rod operatively engaging the supply valve 22 within a recess 59 formed in its face.

For the purpose of operating the plunger 53 a cam 6| is provided, having a peripheral face for engaging the end of the plunger 53 and mounted upon a shaft 62 that is supported by a step bearing 63 and a sleeve bearing 64, and that extends upwardly through the cover of the valve casing and is provided with an operating handle 65.

When the handle 65 and the cam 6| are in their release positions, as shown in Figs. 2, 3

and 4, the spring 25 forces the supply valve 22 to its seated position, and the spring forces the release valve 42 toward the left, or to its unseated position. It will be appreciated that the force of the release valve spring 48 is less than the force of the supply valve spring 25, which is less than the force of the regulating spring 39. When the handle 65 is moved from release position the cam 6| forces the plunger 53 toward the right, the first portion of this movement effecting a compression of the spring 48 and the seating of the release valve 42, closing communication between the pressure chamber l8 and the atmosphere through passages 4|, 44 and 38. Further movement of the plunger 53 toward the right causes the spaced levers 5| to pivot about their lower ends, further movement of the roller 56 toward the right being prevented by the regulating spring 39, and causes the rod 53 to force the supply valve 22 against the compression of the supply valve spring 25 to open communication between supply pipe 8 and the pressure chamber l8, through passage 2| and supply chamber 20, thus supplying fluid under pressure from supply pipe to the pipe I?! leading to the pressure control rheostat 6.

The amount of fluid under pressure supplied to the pressure chamber |8,,and to the pipe |9, is dependent upon the degree of movement of the cam 6| from its release position, since while the pressure within the chamber |8 increases due to flow of air thereto through the supply valve 22 a pressure exert-ed on the chamber side of the piston 35 in opposition to the pressure exerted by the regulating spring 39, This pressure continues to build up until it becomes sufiicient to force the piston 35 toward the right, relieving the pressure on the roller 56 and permitting the supply valve spring 25 to force the rod 56 toward the left, pivoting the levers 5| about the pivot pin 52 and moving the supply valve 22 into engagement with its seat 24. The amount of pressure on the chamber side of the piston 35 necessary to effect sul'licient movement of piston 35 to cause the supply valve 22 to seat is dependent upon the amount of movement of the handle 65 and of the cam 6| away from its release position. The greater the movement of the cam from its release position the greater will be the movement of the pivot pin 52 toward the right, and, consequently, the greater will be the compression of the regulating spring 39 necessary to permit movement of the levers 5|, and of the rod 58 to effect the seating of the supply valve 22. It will be apparent therefore that the brake valve device is self-lapping on a pressure basis, the degree of pressure within the pressure chamber 5 3 and the pipe l9 necessary to eii'ect lap operation of the valves being dependent upon the degree of movement of the handle 65 from its release position.

In order to provide for emergency operation of the brakes an emergency valve 65 is provided in an emergency valve chamber 61 located in the upper part of the main casing portion M for controlling communication between the emergency pipe |2, with which the emergency valve chamher 5'! is in open communication through the passage 68, and the atmosphere through the exhaust chamber 69 and exhaust port 1|. A spring i2 is provided in the emergency valve chamber that engages the emergency valve 65 urging it to its seated position. A valve stem 13 is provided for the valve 65 that extends through a bore between the emergency valve chamber 6! and the exhaust chamber 69, and is positioned to' be engaged by movement of a cam 14 positioned on the shaft 52, when the handle is rotated to emergency position as best shown in Fig. 5, thus opening communication between the emergency pipe l2 and the atmosphere to effect an emergency operation of the brakes in a manner to be later explained.

A sanding valve 15 is provided within the sanding valve chamber 76 in the upper part of the casing structure that is in open communication with the supply pipe 8 through passages I1 and 2!, and with the sanding pipe 13 through chamber 79 and passage 8|. A spring 82 is provided in the sanding valve chamber for urging the sanding valve '55 to its seated position, and a valve stem 83 is provided that extends upwardly from the valve I5 through an opening in the cover portion of the casing, and beyond the face thereof, into engagement with an operating ring 34, pivotally supported by a hinged pin 85 that is carried by upwardly extending lugs 86. The operating ring 84 is adapted to be engaged by a finger 8'5 extending downwardly from the handle which may be actuated about the pivot pin 88, and when so actuated presses the ring 34 and the valve stem 83 downwardly to efiect communication between the supply pipe 8 past the sanding valve iii to the sanding pipe '53. The usual notched plate 89 is provided for defining the several operative positions of the handle 55.

The pipe it! connects the pressure chamber is within the brake valve device I to a piston cham-.

her 9! within the pressure operated rheostat 6. A piston 92 is provided within the piston chamher 9!, having a stem 93 that extends downwardly and engages a rod 94, which extends through an opening in a nut 95 in the lower end of the piston chamber cylinder, and which engages a rheostat arm 95 pivotally supported by a pin 3'1. The arm 96 is actuated by the pressure of the piston 32 acting against the pressure of a spring 38 to operate the rheostat contact member 99 into engagement with one of the contact members associated with the resistor Edi for the voltage applied to the train wire I3.

The self-lapping magnet valve 4 comprises an operating winding I32 and a core member I83 to the lower end of which a diaphragm I34 and a stern I35 are attached, the stem providing a valve seat its for a release valve I31 positioned within a release valve chamber I39 for controlling communication between the chamber I39 and an outlet chamber I08, that is connected to the atmosphere through outlet port III. A spring H2 is provided within the release valve chamber I39 for urging the stem I95 and the core IE3 upwardly to unseat the valve I01 and effect communication between the application and release pipe i I3 connected to the control device 3 and the atmosphere. A valve I I 5 is provided in axial alignment with the valve 91 having a seat in a partition wall II5 of the casing, and is provided with an upwardly extending stem I I8 which extends through a bore in said well and engages the valve Idl. The valve H4 controls communication between the application valve chamber II! that is connected to the supply pipe 8 through the branch pipe H3, and the release valve chamber I89 that is connected to the application and release pipe 553. A sprng H9 is provided within the chamber I I! for urging the valve II4 to its seat and a stop I 20 is provided in the lower part of the casing structure to limit the downward movement of the valve H4. The upward movement of the core I03 is limited by a stop I2I in the form of a bolt inserted through the upper wall of the casing structure, and its downward movement is limited by a nut I23 screw-threadedly attached to the core and adapted to engage a flanged washer I24 attached to the casing.

Upon energization of the winding I82, the core I03 is moved downwardly bringing the seat I36 against the valve I01 to close communication between the release valve chamber I33 and the outlet chamber I08, and, upon further downward movement of the core, to force the valve lid from its seat thus opening communication etween the chamber II! and the chamber I39. Fluid under pressure thus passes from the supply pipe 8 through branch pipe IIB, chamber ill, chamber I 39, application and release pipe M3, to efiect application or" the brakes. As fluid under pressure enters the chamber I39 the pressure of this fluid against the diaphragm I64 tends to urge the core H33 upwardly causing the valve H4 to seat when the pressure within the chainber I89 has become equal to or greater than the downward force of the magnet. The particular pressure at which the valve I I4 will seat depends, therefore, upon the degree of energization of the winding IE2.

The control valve device 3 comprises an emergency valve portion I3I, a relay valve portion 132 and a pipe bracket portion I33. The relay valve por ion comprises a casing having a chamher !34 normally connected to the application and release pipe H3 through passages I35, 536 and the cavity I31 in the emergency slide valve SI, and containing an application piston I32, which is adapted through the medium of a stem 39, to operate a slide valve Hi I, operatively connected to the stern and contained in a valve chamber I42, that is constantly connected to the brake cylinder I through a brake cylinder pipe Q43. Also contained within the casing of the relay valve portion is a fluid pressure supply valve I4 3, that is subject to the pressure of a spring M5, and which is provided with a stem 546 that is adapted to be operatively engaged by end of the piston stem I39.

The relay valve device is shown in its releasing position in which position the application piston I38 and the slide valve iii are in their extreme upper or brake releasing positions. With the slide valve I 45 in this position the valve chamber i 52 and consequently the brake cylinder I is connected to the atmosphere through an exhaust passage and pipe I47. With the application piston I33 in release position the stem I33 will be out of engagement with the end of the supply valve stem I46 so that the pressure or" the spring I45 will maintain the supply valve E i-t seated against its rib seat I48, thereby maintaining communication closed from the chamber 3 that is constantly connected to the supply reser voir 2 through passage and pipe IEI, to the valve chamber I42. A baffle piston I53 is provided on the piston stem I39 and defines a chamber 152 at the lower side of the application piston i that is in communication with the valve chamber I l-2 through a restricted passage I54. The bafiile piston prevents changes in pressure within the valve chamber I42 from being too rapidly applied to the lower side of the application piston which, under some conditions, might cause a pumping action of the relay valve.

The emergency valve portion comprises a casing having a chamber I55 that is in constant communication, through passage and pipe I 55,

til

with the emergency pipe I2, and that contains a piston I5! that is urged by a spring I58 toits lower or illustrated position. I'he piston is provided with a stem I59 that operatively engages an emergency slide valve Ifil, contained Within a slide valve chamber I62 that is in constant communication with the supply pipe 8 through passages 563, IE4 and branch pipe I65. In the release or illustrated. position of the emergency piston I5"! and valve IGI, the release and. application pipe H3 is in communication with the application piston chamber I 34 of the relay valve device through groove I37 in the emergency valve I6I, the sanding reservoir I66 is in communication with the valve chamber I62 through pipe I61, passage I68, and port 569 in the emergency valve ISI. A sanding pipe I?! is adapted to be connected to the sanding reservoir I69 through a one-Way check valve 512, pipe I13, passage I14 and cavity IE5 in the emergency slide valve I6I when the valve is so positioned that the cavity I'I5 connects the passages I'M and I58.

Upon operation of the pressure controlled rheostat to cause engagement of the contact member 99 with one of the contact members associated with the resistor IGI the train wire I3 is connected to the constant voltage source of electrical energy 5 o gh conductor I8I, resistor I32, contact mei and a portion of the resistor lfil. Operating circuits will now be completed from the train wire I9 through the windings I92 of the several self-lapping magnet valves associated with the train units. This circuit ex tends from th wire I3 through conductor I83, the winding I92 of the self-lapping magnet valve, conductor resistor F65, and contact arm I86 oi the load regulating device contact segment I81, and conductor I89 to ground, and to the grounded terminal I99 or the source 5. In order to prevent an operation of the rheostat for varying the resistance from changing the voltage between the train wire I3 and ground, a circult is provided on each train unit between the train wire I6 and ground in shunt relation to the circuit of the winding of the s i-lapping magnet valve device T---s circuit extends from the junction point I9| through conductor I92, a resistor I93 to a variable resistor I94, and by Contact arm se 'it 59? and conductor I88 to ground. re .stor 599 is designed to have the same resistance as the winding I of the self-lapping magnet valve and the resistors I and Hit are equal and provided with equal resistance steps. Consequently as the contact arm I86 is moved to the rignt or to the left the resistance dropped from one of the two pairs of circuits will be added to the other of the two pairs of circuits, and, since the resistor I93 and the winding I92 of the self-lapping valve have equal resistance, the c it flowing from the junction point to I through conductor I29 will be constant any position of the arm I8? and for a given voltage between the train wire l3 and ground. The voltage between the train wire I3 and ground, and consequently the degree of energization of the winding I92 of the self-lapping magnet valve will therefore depend solely upon the position of the contact member 99 of the pressure rheostat 6 that determines the amount of the resistor I95 that is connected in circuit between the constant voltage source of supply :3 and the train wire I3.

The variable load brake mechanism I4 comprises a plunger I9! that is connected by a pivot pin I98 to one end of a bell crank lever I99 that is pivotally mounted on the pin 29I for operating the contact arm I86. The lower end of the plunger I9! is provided with an arm 292 that is subject on one side to the pressure of a spring 203, and, on the other side to the pressure of a 5 spring 294, that engages the arm 292 and the upper and lower portions of the supporting structure 295 carried on the spring flange of the car truck 296. The variable load brake mechanism is also provided with a cylinder 268 mounted on 10 the car body and upon which the bell crank lever I99 is supported. In order to maintain the plunger I91 in its position of adjustment according to the load on the car and against movement due to vibration of the car body with respect to the 15 truck, the lever I99 is provided with a down wardly extending portion 269 that operatively engages a pin 2I9 carried by the rod 2 that is connected between pistons 2I2 and ZIS, within the casing 298, and provided, respectively, with 20 which the movable contact arm I86 is connected, 30

and which performs the same function as the resistors I85 and I94 shown in Fig. 1, nameiy tow vary the degree of energization of the operating winding I92 of the self-lapping magnet valve device 1 in accordance with the load on the 9 or train unit, without varying the flow of canrent between the train wire I3 and ground.

The several figures of the drawings illustrate the several parts of the equipment in brake r leasing or charging position. In this position of 40 the various parts of the equipment, the system may be charged by the flow of fluid under pressure from the main reservoir 9 through the feed valve II to the supply pipe 8. Fluid under pressure flows through the supply pipe 8 to the sev- 45 eral train units, and, in each unit, through branch pipe I65 leading to the control valve device through passage I64 and pipe I5I to charge the supply reservoir 2. Fluid under pressure also flows from passage I64 into the chamber of the supply valve device associated with the relay valve portion I32, and from the passage I64 through passage I63 to the emergency valve chamber I62. The sanding reservoirs I charged by the flow of fluid under pressure 55 the emergency valve chamber I62 through port I69 in the emergency valve, passage 58, and sanding reservoir pipe I61. The emergency p" I2 is charged by the flow of fluid under pre ure from the supply pipe 6 through a restricted sage 22I in the bracket section of the brake v? device I, thus charging the emergency pis chamber I55 from the emergency pipe l2 through branch pipe and passage I56. When the en: gency piston I51 is in its lower or illustra position, the piston chamber I55 and the valve chamber I62 are in communication thi restricted feed groove 222 around the piston W thus permitting the emergency piston chamber I55 to also be charged from the emergency valve chamber I62 unless the pressure differential between the valve chamber I62 and the piston chamber I55 becomes suflicient to cause the piston I51 to move upwardly against the downward pressure of the spring I58. 75

If the operator desires to apply the brakes, the brake valve handle 65 may be moved into any position within its service application zone, thus permitting fluid under pressure .to pass from the supply pipe 8, past the supply valve 22, into the pressure chamber I8 within the brake valve device I until the pressure within the chamber I8, and within the chamber SI of the pressure operated rheostat 6, builds up to a value dependent upon the degree of movement of the brake valve handle 55 from its release position in the manner hereinbeiore described. The rheostat 6 is operated to move the contact member 99 downwardly into engagement with one of the contact members associated with the resistor I ill, the degree of movement being dependent upon the amount of pressure within the piston chamber 9I. This operation of the rheostat 6 causes the train wire I3 to become alive, the voltage between the train wire I3 and ground being dependent upcn the amount of the resistance lei that is in circuit between the constant voltage source 5' and the train wire I3, and thus controls the degree of energization of the windings M3 for operating the self-lapping magnet valve devices 4.

The degree of energization of the winding I02 is also determined in part by the position of the contact arm I86 on the resistor I85. When the car is unloaded the arm I85 is in its extreme left position thus including the entire resistance I85 in circuit with the winding I02 and effecting a lesser degree of energization of the winding for a particular voltage drop between the wire I3 and ground. If the car is loaded the additional weight causes the car body and the casing portion 238 to be lowered with respect to the car truck, thus effecting operation of the contact arm I85 toward the right an amount depending upon the degree of loading of the car. The winding 62 of the self-lapping magnet valve will therefore be energized an amount depending in part upon the loading of the car, the energization being greater for a heavily loaded car than for a lighter loaded car.

As explained above the amount of fluid under pressure admitted from the supply pipe 8 into the application and release pipe H3, through the application valve chamber Ill and the release valve chamber I 09 of the self-lapping magnet valve device 4, is dependent upon the degree of energization of the winding I62. Fluid under pressure passes from the application and release pipe I I3, through passage I36 in the control valve device, cavity I31 in the emergency valve I6I, passage I35 to the application piston chamber 34 of the relay valve device, forcing the piston 33 together with its stern I39 downwardly until the end of the stem engages the stem I43 of the supply valve I46. As the slide valve I4I moves downwardly, the ports 223 and 224 providing communication between the valve chamber I42 and the chamber 225 and the exhaust pipe Ml, are lapped, thus closing communication between the brake cylinder I and the atmosphere. Upon a further downward movement of the piston I38, and its stem I39, the supply valve I44 is unseated permitting the flow of fluid under pressure from the supply reservoir 2 through the supply reservoir pipe I5I to chamber I49, past the supply valve I44 into the slide valve chamber I42, and to the brake cylinder through the brake cylinder pipe I43, thus effecting an application of the brakes. As the pressure builds up in the slide valve chamber I 42, the pressure on the under side of the application piston I38 and on the baflle piston I53 will also build up, the pressure in the chamber I52 building up more slowly than the pressure in the valve chamber I42 by virtue of the restricted port I52 through the baffle piston I53, thus preventing the relay valve device from pumping, first to a valve open and then to a valve closed position. When the pressure in the chamber I52 has built up to be equal to the pressure within the piston chamber I34 the piston stem I33 will be forced upwardly by the pressure of the spring I45 until the valve I44 engages its rib seat M8, after which there will be no further upward pressure of the valve stem I46 against the piston stem I39. The relay slide valve I 4| will then be in lap position with the fluid under pressure within the brake cylinder at a pressure corresponding to the pressure within .the application piston chamber I34.

Should the operator desire an emergency operation of the braking equipment, the handle 65 is moved to its emergency position, thus eifecting operation of the cam I4 into engagement with the emergency valve stem 13 to move the emergency valve 66 from its seat against the bias of the spring I2 as shown in Fig. 5. Fluid under pressure is then vented from the emergency pipe I2 through passage 68, emergency valve chamber 6?, past the emergency valve into the exhaust chamber 69, and through the exhaust passage II to the atmosphere, causing the pressure in the emergency piston chamber I55 to be rapidly reduced. This reduction in pressure within the emergency valve piston chamber I55 takes place at too rapid a rate to permit the chamber I55 from being charged through the feed groove 222 around the piston, thus creating a high differential in pressure between the valve chamber i62 and the chamber I55 and operating the piston I57 upwardly against the pressure of the spring I53. This upward movement of the emergency piston I5l causes the emergency slide valve I6I to move upwardly until the port "I 69 in the valve registers with the passage I35 leading to the application piston chamber I34 of the relay valve, thus directly connecting the piston chamber I34, through the emergency valve chamber I62 and passages I63, I64 and pipe I65, to the supply pipe 8 to bring the pressure within the chamber I34 up to the supply pipe pressure. The application piston I36 and the piston stem I39 are thus forced downwardly to cause operation of the supply valve I44 to eirect communication between the brake cylinder I and the supply reservoir 2 until the pressure in the brake cylinder has been built up to the full reservoir pressure.

When the emergency valve I-IiI is moved to emergency position, communication is established between the sanding reservior I66 on the first train unit and the sanding pipe I'II through the cavity H5 in the emergency valve that is positioned to connect the passages I14 and I68. In the same manner fluid under pressure is supplied to sanding devices on other train units from the from the supply pipe 8 through passages 2|, 11, 8| and pipe '58 to the sanding pipe I'll.

It will be understood from the above description that for all positions of the brake handle 65 within its service application zone the degree of braking of the train is dependent upon the positioning of the handle which controls the degree of energization of the winding I02 of the selflapping magnet valve devices 4 and that the energization of the individual self-lapping magnet valve on the individual car units of the train is also determined in part by the position of the variable load control mechanism I4 that is dependent upon the loading of the individual car, thus effecting a greater brake cylinder pressure for a heavily loaded car than for a lightly loaded car to effect a substantially constant rate of retardation of the several cars independently of their loading.

While I have illustrated and described one preferred embodiment of my invention, it will be apparent to those skilled in the art that many modifications thereof may be made within the spirit of my invention and I do not wish to be limited otherwise than by the scope of the appended claims.

Having now described my invention, what I claim as new and desire to secure by Letters Patent, is:

1. In an electropneumatic brake equipment for multiple unit railway trains, in combination, a

brake cylinder for each unit, electroresponsive means operable for controlling the supply of fluid under pressure to, and the release of fluid under pressure from, said brake cylinder in accordance with the degree of energization thereof, of manually operable control means operative in accordance with its position within a service application zone for effecting varying degrees of energization of the electroresponsive means, and means responsive to the load on each unit for effecting a relatively greater application of the brakes for a relatively heavier load on that unit only.

2. In an electropneumatic brake equipment for multiple unit railway trains, in combination, a brake cylinder for each unit, electroresponsive means operable for controlling the supply of fluid under pressure to, and the release of fluid under pressure from, said brake cylinder in accordance with the degree of energization thereof, of manually operable control means operative in accordance with its position within a service application zone for effecting varying degrees of energization of the electroresponsive means, resistor means associated with each electroresponsive means, and means for decreasing the resistance of said resistor means in accordance with increasing load on the unit to effect a greater degree of application of the brakes on the unit for a given operation of the manually operable means.

3. In a brake equipment for multiple unit railway trains, a brake cylinder associated with each unit, valve means associated with each brake cylinder for controlling the flow of fluid under pressure to and from the brake cylinder, electrical means for controlling said valve means, and resistor means in series circuit relation with said electrical means and responsive to the load on the unit for modifying a condition of the operating circuit only of said electrical means.

4. In a brake equipment for multiple unit railway trains, braking means associated with each unit, electrical means associated with each train unit for controlling the operation of said braking means, and means responsive to the load on each unit for modifying an operative condition of the operating circuit only of the electrical means associated with that unit.

5. In a brake equipment for multiple unit railway trains, in combination, braking means associated with each train unit, electrical means for each unit for controlling the operation of said braking means and operable to effect a degree of application of the brakes in accordance with the voltage impressed thereon, and resistor means in circuit with said electrical means and responsive to the load on said unit for effecting the application of an increasing voltage only on the electrical means of the associated unit as the load on the vehicle increases.

6. In a fluid pressure brake, in combination,

electroresponsive means operative to supply fluid under pressure to effect an application of the brakes, a manually operable self-lapping brake valve device for controlling the energization of said electroresponsive means in accordance with its position within an application zone to effect a desired degree of application of the brakes, and means for controlling the degree of energization of said electroresponsive means in accordance with the load on the vehicle.

'7. In a fluid pressure brake, the combination with electroresponsive means operative according to the degree of energization thereof for controlling the supply of fluid under pressure for effecting an application of the brakes, of fluid pressure controlled means for varying the degree of energization of said electroresponsive means, manually controlled means for varying the fluid pressure on said fluid pressure controlled means, and means responsive to the load on the vehicle zii for also varying the degree of energization of 55 said electroresponsive means.

CLYDE C. FARMER- 

